EP2302201B1 - Pumpe-System mit Rückgewinnung von Energie - Google Patents

Pumpe-System mit Rückgewinnung von Energie Download PDF

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Publication number
EP2302201B1
EP2302201B1 EP10181357.4A EP10181357A EP2302201B1 EP 2302201 B1 EP2302201 B1 EP 2302201B1 EP 10181357 A EP10181357 A EP 10181357A EP 2302201 B1 EP2302201 B1 EP 2302201B1
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EP
European Patent Office
Prior art keywords
pump
turbine
impellers
pressurization
axial thrust
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Not-in-force
Application number
EP10181357.4A
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English (en)
French (fr)
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EP2302201A3 (de
EP2302201A2 (de
EP2302201B8 (de
Inventor
Hiroaki Yoda
Yoshimasa Chiba
Takanori Ishii
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Hitachi Ltd
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Hitachi Plant Technologies Ltd
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Publication date
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Publication of EP2302201A2 publication Critical patent/EP2302201A2/de
Publication of EP2302201A3 publication Critical patent/EP2302201A3/de
Publication of EP2302201B1 publication Critical patent/EP2302201B1/de
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Publication of EP2302201B8 publication Critical patent/EP2302201B8/de
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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F03—MACHINES OR ENGINES FOR LIQUIDS; WIND, SPRING, OR WEIGHT MOTORS; PRODUCING MECHANICAL POWER OR A REACTIVE PROPULSIVE THRUST, NOT OTHERWISE PROVIDED FOR
    • F03B—MACHINES OR ENGINES FOR LIQUIDS
    • F03B3/00—Machines or engines of reaction type; Parts or details peculiar thereto
    • F03B3/02—Machines or engines of reaction type; Parts or details peculiar thereto with radial flow at high-pressure side and axial flow at low-pressure side of rotors, e.g. Francis turbines
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D13/00—Pumping installations or systems
    • F04D13/02—Units comprising pumps and their driving means
    • F04D13/04—Units comprising pumps and their driving means the pump being fluid driven
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
    • F05B—INDEXING SCHEME RELATING TO WIND, SPRING, WEIGHT, INERTIA OR LIKE MOTORS, TO MACHINES OR ENGINES FOR LIQUIDS COVERED BY SUBCLASSES F03B, F03D AND F03G
    • F05B2220/00—Application
    • F05B2220/60—Application making use of surplus or waste energy
    • F05B2220/602—Application making use of surplus or waste energy with energy recovery turbines
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
    • F05B—INDEXING SCHEME RELATING TO WIND, SPRING, WEIGHT, INERTIA OR LIKE MOTORS, TO MACHINES OR ENGINES FOR LIQUIDS COVERED BY SUBCLASSES F03B, F03D AND F03G
    • F05B2220/00—Application
    • F05B2220/62—Application for desalination
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
    • Y02B—CLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO BUILDINGS, e.g. HOUSING, HOUSE APPLIANCES OR RELATED END-USER APPLICATIONS
    • Y02B10/00—Integration of renewable energy sources in buildings
    • Y02B10/50—Hydropower in dwellings
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
    • Y02E—REDUCTION OF GREENHOUSE GAS [GHG] EMISSIONS, RELATED TO ENERGY GENERATION, TRANSMISSION OR DISTRIBUTION
    • Y02E10/00—Energy generation through renewable energy sources
    • Y02E10/20—Hydro energy

Definitions

  • the present invention relates to a pump system having an energy recovery apparatus used in, e.g., a seawater desalination plant to recover power from energy of concentrated water.
  • a pump system as described in the preamble portion of patent claim 1 has been known from IT 1272453 B .
  • seawater desalination plants The market for seawater desalination plants is expected to expand because of, e.g., a growing worldwide need for water and water shortage due to climate change. Water supplied from seawater desalination plants is important for infrastructure. Therefore, reduction of desalination cost and maintenance of water quality for drinking are desirable. Particularly in the reduction of the desalination cost, higher efficiency is desirable for reduction in plant cost and running cost of a reverse osmosis membrane pressurization pump that consumes about fifty percent of electrical energy supplied to the plant.
  • reverse osmosis membrane pressurization pumps have a discharge quantity of 600 to 3, 000 m 3 /h, a net pump head of 550 to 740 m, and a pump shaft power of 1,000 to 6,000 kW.
  • the reverse osmosis membrane pressurization pumps use multistage centrifugal diffuser pumps.
  • Pelton turbines are used in the energy recovery apparatus using concentrated water. As discussed in JP 6-210140 A , in the usage of energy of concentrated water, an output shaft of the Pelton turbine is coupled to a main shaft of a motor driving a pressurization pump to use rotational energy recovered by the Pelton turbine as part of driving force for the pressurization pump. In such a way, energy saving for the pressurization pump is achieved.
  • An amount and pressure of the concentrated water is about 300 to 1,800 m 3 /h
  • the head is 500 to 700 m
  • its energy is about 500 to 3,600 kW, which is large to reach about 40 to 60 percent of the pressurization pump driving force.
  • IT 272452 B discloses a pump system having an energy recover apparatus, the pump system comprising a pressurization pump; and a hydro turbine used for the energy recover apparatus, the energy recover apparatus recovering energy from high-pressure concentrated waste water to use the energy as driving force for the pressurization pump when raw water pressurized by the pressurization pump is filtered by a reverse osmosis membrane, the hydro turbine having multistage turbine impellers coaxial with a rotation shaft of the pressurization pump, the turbine impellers being disposed opposite pump impellers of the pressurization pump.
  • the present invention is a pump system having an energy recovery apparatus which recovers energy from high-pressure concentrated waste water through a reverse osmosis membrane to use the energy as driving force for the pressurization pump when raw water pressurized by a pressurization pump is filtered by the reverse osmosis membrane.
  • the energy recovery apparatus uses a hydro turbine having multistage turbine impellers coaxial with a rotation shaft of the pressurization pump. The turbine impellers are disposed opposite pump impellers of the pressurization pump.
  • the pump system having the energy recovery apparatus includes an axial thrust support device which supports an axial thrust of the turbine impellers and an axial thrust of the pump impellers.
  • the pressurization pump and the hydro turbine are disposed to position an inlet side (low pressure side) of the pressurization pump and an outlet side (low pressure side) of the hydro turbine adjacent one another.
  • the rotation shaft for the pressurization pump and hydro turbine is supported by a radial submerged bearing.
  • the axial thrust support device is an axial thrust balancing device using a balancing disc.
  • an end of the rotation shaft for the pressurization pump and hydro turbine has a non-seal structure using an end cover.
  • a pressurization pump and an energy recovery apparatus are integrated to obtain compactness and higher efficiency.
  • a multistage turbine is used as the energy recovery apparatus. Accordingly, unlike a Pelton turbine, not only a pump portion but a turbine portion do not need to be mounted higher than a liquid level for discharging water, and a height of a mounting surface for the apparatus can be made low. As a result, it becomes easier to ensure capability of an inlet of the pump.
  • an amount of desalination is favorably equal to or over 5,000 to 10,000 m 3 /day per a single row (per one reverse osmosis membrane pressurization pump) as an applicable plant size.
  • FIG. 3 shows a pressurization pump 100 using a centrifugal pump, a Francis turbine 200 (hydro turbine) as an energy recovery apparatus disposed below the pressurization pump 100 to recover power energy, a rotation shaft 1 common to the pressurization pump 100 and hydro turbine 200, an axial thrust support device 300 for supporting the axial thrust of rotation of both the pump and turbine, and a high-pressure reverse osmosis membrane unit 50 for removing impurity from raw water including impurity such as salt through an osmosis membrane process.
  • a pressurization pump 100 using a centrifugal pump a Francis turbine 200 (hydro turbine) as an energy recovery apparatus disposed below the pressurization pump 100 to recover power energy
  • a rotation shaft 1 common to the pressurization pump 100 and hydro turbine 200
  • an axial thrust support device 300 for supporting the axial thrust of rotation of both the pump and turbine
  • a high-pressure reverse osmosis membrane unit 50 for removing impurity from raw water including impurity such as salt through an os
  • the rotation shaft 1 rotates, raw water 51 including impurity such as salt is drawn from a pump inlet 3, discharged from an outlet 8, and supplied to the high-pressure reverse osmosis membrane unit 50.
  • the high-pressure reverse osmosis membrane unit 50 applies a reverse osmosis membrane process to the raw water 51 including impurity such as salt, and discharges permeate water 52 from which impurity such as salt has been removed.
  • high-pressure concentrated water 53 which has been left by the reverse osmosis membrane process, is supplied to a turbine inlet of the turbine 200, and recovered as part of energy for driving (rotating) this turbine. Concentrated water 54 from which energy has been recovered in the turbine section is then discarded from a turbine outlet 36 outside the system.
  • Embodiment 1 of the pump system of the present invention is explained in reference to a cross section of Fig. 1 .
  • the rotation shaft 1 common to the centrifugal pressurization pump 100 and Francis turbine 200 is a vertical shaft
  • the pressurization pump 100 is disposed above the Francis turbine (hydro turbine) 200 which recovers energy
  • the axial thrust support device 300 supports an axial thrust acting on pump impellers of the pressurization pump 100 and an axial thrust acting on turbine impellers of the hydro turbine 200.
  • the rotation shaft 1 is a rotation shaft common to the pressurization pump 100, turbine 200, and axial thrust support device 300, and described as a shaft 1a in the pressurization pump and as a shaft 1b in the turbine.
  • the pressurization pump 100 includes, in a pump casing 13, two stages of centrifugal impellers 4a (first stage pump impeller) and 4b (second stage pump impeller), and diffusers 5a and 5b disposed to respective peripheral outlets of the pump impellers 4a and 4b.
  • the pump inlet 3 in communication with the impeller 4a is provided to a lower portion of the casing 13.
  • the outlet 8 in communication with the impeller 4b is provided to an upper portion of the casing 13.
  • a static fluid path 6 having a square bracket shape connects between the first and second stage impellers.
  • Return vanes 6a are disposed radially from the shaft center in the radial direction to straighten a flow to the next stage impeller.
  • multistage pump impellers (two stage impellers in this Embodiment) are provided to a pump, a net pump head of which is high to be about 500 to 800 m.
  • Pump driving power is applied to the pump rotation shaft 1a via a shaft coupling 2 from, e.g., an electric motor (not shown).
  • the pressurization pump 100 draws the seawater 51 as raw water from the inlet 3.
  • a pressure of the seawater 51 is raised at the first and second stage pump impellers 4a and 4b.
  • the diffusers 5a and 5b change kinetic energy of the flow to pressure energy.
  • the seawater 51 flows from the first stage to second stage through the static fluid path 6 having a square bracket shape, and the flow to the next stage is straightened by the return vanes 6a.
  • the flow which has come out of the second stage impeller 4b is gathered to a concentric space 7 via the diffuser 5b, and discharged from the outlet 8.
  • the pump shaft 1a is supported radially by a bearing 9a disposed to a lower end of the pump inlet 3 and an upper bearing 9b of the pump shaft 1a.
  • These bearings are submerged bearings formed of a self-lubricating material (for example, a Poly-Ether-Ether-Ketone (PEEK) resin material).
  • PEEK Poly-Ether-Ether-Ketone
  • Each bearing can function as a bearing by a property of the self-lubricating material and by lubrication of a self lubricant.
  • a great downward axial thrust generated in the pump impellers 4a and 4b at the time of rotation of the pump is balanced by an automatic axial thrust balancing device 10 not to act the axial thrust on a thrust bearing 11.
  • the thrust bearing 11 may be a bearing for supporting a self-weight of the pump rotor when the pump is at rest.
  • a ball bearing is used as the thrust bearing 11, an inner ring of the ball bearing is secured to the shaft 1, and the outer ring is fitted movably in the axial direction.
  • a stationary stopper 11a on a lower side of a case of the bearing supports the self-weight of the pump rotor via the ball bearing 11.
  • a shaft seal for a penetration portion of the pump shaft 1a to the atmosphere a leakage flow largely depressurized from a discharge pressure of the pump through the automatic axial thrust balancing device 10 is sealed by a shaft seal 12 such as a gland seal. The leakage flow is returned to the pump inlet 3 via piping (not shown).
  • the axial thrust support device 300 includes the axial thrust balancing device 10 and thrust bearing 11, and is provided to an upper portion of the rotation shaft 1 in the pump casing 13.
  • Equation 1 Ns shows a hydro turbine specific speed
  • N shows hydro turbine revolutions per minute (rpm)
  • Q shows Hydro turbine flow rate (m 3 /min)
  • H shows an effective head (m).
  • rpm hydro turbine revolutions per minute
  • m Hydro turbine flow rate
  • m Hydro turbine flow rate
  • H an effective head
  • the turbine impellers including a turbine impeller 34a (the first stage turbine impeller), a turbine impeller 34b (the second stage turbine impeller), and a turbine impeller 34c (the third stage turbine impeller), are coaxially disposed within the turbine casing 39 opposite the pump impellers 4a and 4b (facing the impellers to each other).
  • Guide vanes 33a (the first stage guide vanes), 33b (the second stage guide vanes), and 33c (the third stage guide vanes) are disposed to respective guide portions to the turbine impellers to straighten a fluid flow flowing to each turbine impeller 34 and to regulate a direction of the flow.
  • a water path 35 is interposed between each stage to provide return vanes 35a and return vanes 35b.
  • the return vanes prevent the flow which has come out of each turbine impeller from swirling, and straighten the flow.
  • the turbine inlet 31 in communication with the turbine impeller 34a is disposed to a lower portion of the casing 39.
  • the turbine outlet 36 in communication with the turbine impeller 34c is disposed to an upper portion of the casing 39.
  • the turbine 200 is mounted below the pressurization pump 100 to position the pump inlet 3 of the pump casing 13 and the turbine outlet 36 of the turbine casing 39 adjacently to one another. In such a way, a specific seal mechanism is unnecessary for a connection portion between the pump inlet 3 of the pressurization pump 100 and the turbine outlet 36 of the turbine 200, because the pump inlet 3 and the turbine outlet 36 are both on the low pressure side and have a low differential pressure therebetween.
  • the water 53 is straightened and a direction of the flow of the water 53 is regulated.
  • the water 53 flows into the first stage impeller 34a to change energy of one third of the effective head into mechanical power.
  • the water 53 flows through the return vanes 35a and water path 35 and flows into the second stage impeller 34b through the second stage guide vanes 33b.
  • the water 53 flows through the return vanes 35b and water path 35 and flows into the third stage impeller 34c through the third stage guide vanes 33b.
  • the energy of the effective head is changed at the third stage impeller 34 c , the water 53 is discharged from the turbine outlet 36 outside the turbine.
  • Equation 2 D C ⁇ 2 ⁇ gH N 60 ⁇ ⁇
  • Equation 2 D shows an outer diameter of a turbine impeller, C shows a peripheral velocity coefficient of a turbine impeller (dimensionless number) , H shows an effective head per one stage (m), and N shows revolutions per minute (rpm) of a turbine impeller.
  • An axial thrust F is calculable by Equation (3). Equation 3 F ⁇ n ⁇ ⁇ 4 ⁇ D 2 ⁇ ⁇ ⁇ gH
  • Equation 3 F shows an axial thrust (N), n shows the number of hydro turbine stages, ⁇ shows a density (kg/m 3 ) of seawater, g shows a gravitational acceleration (m/s2), and H shows an effective head per one hydro turbine stage. Since the number of the stages of the turbine impellers is greater than that of the pressurization pump, an effective head per one turbine impeller is smaller than a net pump head per one stage of the pump. At the same time, given that a peripheral velocity coefficient of the turbine impeller is usually smaller than that of the pump impeller, an outer diameter of the turbine impeller is smaller than that of the pump impeller. Therefore, as shown in Equation (3), since the turbine and pump are generally the same in (n*H), an axial thrust of the turbine 200 is smaller than an outer diameter of the pump impeller due to an outer diameter of the turbine impeller.
  • a downward axial thrust of the pump impeller is partially cancelled by an upward axial thrust of the turbine impeller, and thus becomes smaller.
  • This remaining axis thrust which has been made smaller, can be balanced by the axial thrust balancing device 10 of the pump.
  • the turbine shaft 1b is supported by a bearing 37 on a lower end of the turbine shaft 1b and a pump bearing 9a.
  • these bearings are submerged bearings as well as the bearings 9a and 9b of the pump, a bearing lubrication device is unnecessary to achieve easy downsizing and maintenance of the system.
  • a flow rate of the concentrated water 53 in the turbine 200 is obtained by subtracting a reverse osmosis membrane permeate flow from a pump water supply, namely about forty to sixty percent of the pump water supply, and smaller than the pump water supply.
  • a flow direction (angle) of each guide vane is regulated.
  • Fig. 4 is a view explaining relationship between an angle of each turbine guide vane 33 relative to the turbine impeller 34 and an angle of each diffuser 5 of the pump.
  • the diffusers 5 (only part of which is shown) are shown on the assumption that the same impeller as the pump impeller is used as the turbine impeller 34.
  • relationship between these angles is ⁇ t ⁇ p.
  • the concentrated water is guided to the turbine impeller 34 generally at a right angle to transfer energy efficiently even when an amount of the concentrated water guided to the turbine guide vanes 33 is small. Therefore, a specific speed of the turbine impeller can maintain higher than that of the pump impeller to recover energy efficiently.
  • the multistage centrifugal pump as the pressurization pump for the reverse osmosis membrane and the multistage Francis hydro turbine as the concentrated water energy recovery apparatus and by positioning their impellers on a single shaft opposite each other, the compact, efficient, reliable, efficient, high-reliability, low-cost pump system having the energy recovery apparatus is realizable.
  • Embodiment 2 is explained in reference to Fig. 2 .
  • Embodiment 2 is different from Embodiment 1 only in that a rotation shaft is horizontal and an axial thrust support device includes a balance drum 14 and a thrust bearing 15.
  • the balance drum 14 supports axial thrusts of the pump and hydro turbine by use of a difference of pressures respectively acting on front and back surfaces 14a and 14b of the drum 14. In comparison with the axial thrust balancing device of Embodiment 1, the balance drum 14 has no automatic regulation function. Therefore, it is difficult to balance the axial thrusts completely. The remaining thrust is supported by the thrust bearing 15.
  • Embodiment 1 since the axial thrust of the hydro turbine impellers and pump impellers is partially canceled to become small, the same advantage as Embodiment 1 is provided in which an outer diameter of the balance drum 14 can be designed small and leakage loss can be reduced.
  • the thrust bearing 15 uses a material (for example, a Poly-Ether-Ether-Ketone resin (PEEK)) having self-lubricating function, a lubrication device is unnecessary, reducing a cost of the bearing device. Therefore, also in Embodiment 2, like in Embodiment 1, a compact, efficient, reliable, low-cost pump system having a power recovery apparatus can be provided.
  • the vertical shaft structure uses the balancing disc device
  • the horizontal shaft structure uses the balance drum and the thrust bearing, but the vertical shaft structure may use the balance drum and the thrust bearing, and the horizontal shaft structure may use the balancing disc device.
  • the focus of the present invention is to provide a reliable, low-cost axial thrust support device which supports axial thrusts of the pump and hydro turbine and which is shared by the pump and hydro turbine.
  • the above embodiments are applicable for a pump, which is the heart of, for example, a desalination plant using a reverse osmosis membrane.
  • Particularly the embodiments can provide a pump having an energy recovery apparatus preferable for a large capacity desalination plant.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Separation Using Semi-Permeable Membranes (AREA)
  • Structures Of Non-Positive Displacement Pumps (AREA)
  • Hydraulic Turbines (AREA)
  • Other Liquid Machine Or Engine Such As Wave Power Use (AREA)

Claims (6)

  1. Pumpensystem mit einer Energierückgewinnungsvorrichtung, wobei das Pumpensystem aufweist:
    eine Druckerzeugungspumpe (100) mit einem Gehäuse (13) mit einem Einlass (3), und
    eine Wasserturbine (200), die als die Energierückgewinnungsvorrichtung verwendet wird, wobei die Wasserturbine (200) ein Gehäuse (39) mit einem Auslass aufweist, wobei die Energierückgewinnungsvorrichtung Energie von unter hohem Druck stehendem konzentrierten Abwasser rückgewinnt, um die Energie als Antriebskraft für die Druckerzeugungspumpe (100) zu nutzen, wenn Brauchwasser (51), das durch die Druckerzeugungspumpe (100) druckbeauf schlagt wird, mit einer Umkehrosmosemembran (50) gefiltert wird,
    wobei die Wasserturbine (200) mehrstufige Turbinenschaufelräder (34a, 34b, 34c) aufweist, die koaxial zu einer Welle (1) der Druckerzeugungspumpe (100) angeordnet sind, wobei die Turbinenschaufelräder (34a, 34b, 34c) gegenüber den Pumpenschaufelrädern (4a, 4b) der Druckerzeugungspumpe (100) angeordnet sind,
    dadurch gekennzeichnet, dass
    die Wasserturbine (200) unterhalb der Druckerzeugungspumpe (100) montiert ist, um den Pumpeneinlass (13) angrenzend an den Turbinenauslass (36) zu positionieren, und wobei die Anzahl der Stufen der Schaufelräder (34a, 34b, 34c) der Wasserturbine (200) wenigstens gleich oder größer als die Anzahl der Schaufelräder der Pumpe (100) gewählt ist.
  2. Pumpensystem nach Anspruch 1, das ferner eine Axialschubaufnahmevorrichtung (300) aufweist, die einen axialen Schub der Turbinenschaufelräder (34a, 34b, 34c) und einen axialen Schub der Pumpenschaufelräder (4a, 4b) aufnimmt.
  3. Pumpensystem nach Anspruch 1 oder 2, wobei die Druckerzeugungspumpe (100) und die Wasserturbine (200) so angeordnet sind, dass eine Einlassseite (Niederdruckseite) der Druckerzeugungspumpe (100) und eine Auslassseite (Niederdruckseite) der Wasserturbine (200) benachbart zueinander angeordnet sind.
  4. Pumpensystem nach einem der Ansprüche 1 bis 3,
    wobei die Welle (1) für die Druckerzeugungspumpe (100) und die Wasserturbine (200) von einem eingetauchten Radiallager (11) getragen wird.
  5. Pumpensystem nach Anspruch 2,
    wobei die Axialschubaufnahmevorrichtung (300) eine Axialschubausgleichsvorrichtung (10) ist, die eine Ausgleichsscheibe verwendet.
  6. Pumpensystem nach einem der Ansprüche 1 bis 5,
    wobei ein Ende der Welle (1) für die Druckerzeugungspumpe (100) und die Wasserturbine (200) einen nicht abgedichteten Aufbau aufweist, der eine Endabdeckung (38) verwendet.
EP10181357.4A 2009-09-29 2010-09-28 Pumpe-System mit Rückgewinnung von Energie Not-in-force EP2302201B8 (de)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
JP2009224873A JP5344697B2 (ja) 2009-09-29 2009-09-29 エネルギー回収装置を備えたポンプ

Publications (4)

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EP2302201A2 EP2302201A2 (de) 2011-03-30
EP2302201A3 EP2302201A3 (de) 2013-03-13
EP2302201B1 true EP2302201B1 (de) 2014-04-02
EP2302201B8 EP2302201B8 (de) 2014-05-14

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JP (1) JP5344697B2 (de)
KR (1) KR101222384B1 (de)
CN (1) CN102032194A (de)

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CN105604955A (zh) * 2016-01-29 2016-05-25 上海福思特流体机械有限公司 一种立式两级离心煤浆泵
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CN102032194A (zh) 2011-04-27
EP2302201A3 (de) 2013-03-13
EP2302201A2 (de) 2011-03-30
KR20110035920A (ko) 2011-04-06
JP5344697B2 (ja) 2013-11-20
JP2011074785A (ja) 2011-04-14
EP2302201B8 (de) 2014-05-14

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